Feeding and tensioning means for use in web processing apparatus



Jam 11, 1966 o. v. DUTRO ETAL 3,228,623

FEEDING AND TENSIONING MEANS FOR USE IN WEB PROCESSING APPARATUS Original Filed 0G13. 30, 1951 3 Sheets-Sheet l Orville V. Duro By Sherman H. Hewson W J aTTofrEs/s.

Jn. l1, 1966 o. v. DUTRO ETAL FEEDING AND TENSIONING MEANS FOR USE IN WEB PROCESSING APPARATUS 3 Sheets-Sheet 2 Original Filed Oct. 30, 1961 INVENTORS. OrVI//e I/. DUZIO BY Sherman h. Hem/son @ggf rroRA/ft' Jan. ll, 1966 o. v. DUTRo ETAL 3,228,623

FEEDING AND TENSIONING MEANS FOR USE IN WEB PROCESSING APPARATUS original Filed oct. so, 1961 3 sheets-sheet s 'if i Vaca-'E INVENTORS. OrVI//e l/. Duro /1 75 72 BY Sher/mn H. Hem/son nited States Patent Office 3,228,623 Patented Jan. 11, 1966 3,228,623 FEEDING AND TENSIONING MEANS FOR USE IN WEB PRCESSING APPARATUS Orville V. Dutro, 5068 N. Commonwealth, and Sherman H. Hewson, 640 Knight Way, both of La Canada, Calif. Continuation of application Ser. No. 148,766, Oct. 30, 1961. This application Oct. 7, 1963, Ser. No. 315,428 12 Claims. (Cl. 242-75.1)

This invention relates to unreeling mechanisms.

This application is a continuation of applicants copending application, Serial No. 148,766, filed October 30, 1961, entitled Feeding and Tensioning Means for Use in Web Processing Apparatus, now abandoned.

This invention is applicable to the unreeling of a wide variety of materials. While it is also effective for unreeling wire and strip, its principal utility is in connection with unreeling web material, which, as the term is used herein, is flexible material (though not necessarily resilient material), which has a substantial width and an indefinite length. Familiar examples are paper, metal foil, plastic and cloth. For their processing, such as by printing, folding, cutting, and the like, all of these flexible materials have in common the requirement that the material be supplied from a roll at the rate demanded by a machine which subsequently processes it, and at a predetermined and substantially constant tension. The tension and rates of demand and supply are, of course, related, because a difference between these rates is promptly reflected in a slackening or tightening of the material between the take-off point from the roll and the point at which it is supplied to the unit for processing.

It is an object of this invention to provide a device which maintains a close correlation between a demand rate exerted by a processing unit, and the rate at which the material is unreeled from a roll.

It is a related object of this invention to deliver such material at a predetermined tension.

A device according to this invention includes a variable speed driving means which is engageable to the periphery of a roll of material which serves to drive the roll to unreel the material. A tensioning means bears against the material at a location between the take-olf point from the roll and the supply point at which the material is provided for subsequent processing. This tensioning means forms a path loop of variable length under substantially constant tension. Changes in the length of the path loop arise from differences in unreeling and demand rate. The driving means is under control of the tensioning means, whereby the rate of unreeling is adjusted so as to remain equal to that of the demand. This is accomplished by a feedback loop comprising a control over the driving means by the tensioning means, using the length of the path loop as both input and output intelligence.

According to a preferred but optional feature of the invention, the driving means includes an endless geared belt against which the roll bears, and by which it is turned, the gearing on the belts eliminating slippage in the driving means, whereby the possibility of error in output result is also eliminated.

According to still another preferred but optional feature of the invention, the driving means includes a variable speed means, the output of which is adjusted by the tensioning means. In the preferred embodiment, the variability is provided by a split-sheaved pulley whose driving diameter is adjustably Varied by the tensioning means to vary the output of the driving means.

According to still another preferred but optional feature of the invention, the tensioning means derives the force which it applies to the path loop from a constantpressure mechanism whose pressure level is adjustable.

The above and other features of this invention will be fully understood from the following detailed description and the accompanying drawings in which:

FIGURE 1 is a side elevational view of the structure for supporting an elongated web in the form of a roll for use with printing press apparatus (as an example of a use for the device, but not of limitation) an-d illustrating the peripheral drive means for the roll and the variable speed drive mechanism forming a part of the drive means for the roll and operably coupled to the web-tensioning means on the structure, parts being broken away and in section to illustrate details of construction;

FIG. 2 is the opposite side of the roll support structure illustrated in FIG. 1 and showing the means for actuating the peripheral drive means for the roll and the means for actuating the web-tensioning means;

FIG. 3 lis a cross-sectional view taken along line 3-3 of FIG. l; and

FIG. 4 is a cross-sectional, fragmentary view taken along line 4-4 of FIG. 1.

The preferred embodiment of the invention is shown in the drawings, initial reference being had to FIGS. 1 and 2 in which support structure 10 is shown for supporting an elongated web 4initially disposed in the form of a roll 12, includes a pair of spaced walls 14 and v16 mounted above a surface 18 by means of a pair of tracks 20 and 22. Walls 14 and 16 are provided with a pair of opposed, upright marginal edges 24 and 26, and top and bottom edges 28 and 30, respectively. y

Roll 12 is comprised of a web of predetermined thickness and width and adapted for use with printing apparatus capable of performing a number of distinct operations on the web.

Tracks 20 and 22 are each provided with leveling means 32 thereon at the lowermost faces thereof and in engagement with the surface 18 for leveling tracks 20 and 22. A number of cylindrical spa-eers 34 span the distance be-- tween and are secured at the ends thereof to the inner sides of tracks Ztl and 22 to provide stability for tracks 20 and 22, as well as to maintain the same in predetermined spaced relationship throughout the lengths thereof.

Walls 14 and 16 are secured at the bottom edges 30' thereof by a number of lateral-ly extending bolts 36 secured to tracks 20 and 22, respectively, it being noted that the spacing between sides 14 and 16 is less than the spacing between tracks 20 and 22. A number of bars 38 are secured to the inner sides of walls 14 and 16 by means of fastening means (not shown) in the nature of stud bolts. Bars 38 are secured to bars 40 disposed below spacers 34 and aligned with bars 38 by means of bolts 42. By virtue of the aforesaid construction, it is clear that walls 14 and 16 are secured both to tracks 2Q and 22 and to the spacers 34 intermediate tracks 20 and 22.

Each wall 14 and 16 is provided with an elongated, inclined slot 44 therein extending from edge 26 thereof toward edge 24 and terminating centrally of the corresponding wall 14 or 16. An elongated rack 46 is secured to each of the walls 14 and 16 on the innermost surface thereof, rack 46 being provided with upwardly extending teeth 48 thereon which are disposed adjacent and slightly below the edge 50 on the corresponding Wall and deining the lowermost boundary of slot 44. Each rack 46 extends substantially the entire length of slot 44 and terminates at ends 52 as shown in FIG. 3. An elongated strip 54 is secured to the outer surface of each of the walls 14 and 16 and is provided with an upper edge 56 which is disposed within the corresponding slot 44 and is substantially parallel with the corresponding edge 50 of slot 44.

Roll 12 is provided with a cylindrical core 58`which extends substantially through roll 12 and is adapted to com plementally receive a cylindrical drum (not shown) therewithin, it being clear that the drum is preferably presstted in core 58. The drum is provided with opposed ends which journal an elongated shaft 60 to thereby mount shaft 60 on roll 12 for rotation relative to the latter. Shaft 60 projects outwardly in opposed directions from the corresponding sides of roll 12, and each end of shaft 60 is provided with a pinion 62 rigid to shaft 60 and disposed in meshing relationship with the corresponding rack 46. Further, the outermost ends of shaft 60 engage the edges 56 of the corresponding strips 54 and thereby, shaft 60 is partially supported by strip 54 and thus strip 54 assists rack 46 in supporting the entire weight of roll 12. Racks 46 and pinions 62 are provided to assure that the ends of shaft 60 advance equal distances as roll 12 unwinds.

By virtue of the aforesaid construction, roll 12 is biased along the inclined path formed by racks 46, and is caused to move along the path under the action of gravity.

Means for driving roll 12 comprises peripheral drive means broadly denoted by the numeral 64 and disposed adjacent the lowermost ends 52 of racks 46. Drive means 64 includes a pair of spaced shafts 66 and 68 journalled at the ends thereof in bearing means 70 and 72, respectively, it being noted that bearing means 70 and 72 are mounted on the inner sides of Walls 14 and 16. A pair of endless, toothed timing belts '74 are operably coupled with and disposed on aligned pulleys or sprockets 78 rigid to shafts 66 and 68 intermediate the ends of the latter. Belts 74 frictionally engage the periphery of roll 12 and rotate the latter responsive to the rotation of belts 74. A sprocket 78 is operably coupled with shaft 66 and is disposed on the generally outer surface of wall 16. Rotation of sprocket 78 is suicient to rotate shaft 66 to in turn cause belts 74 to rotate roll 12 about the axis of shaft 60.

Guide means is provided on opposed sides of roll 12 adjacent the zone of removal of the web from the latter and includes a pair of rollers 80 and 82 carried by an elongated rod member 84 secured to and spanning the distance between walls 14 and 16. Rollers 80 and 82 are rotatably mounted on the generally uppermost extremities of bases 86 and 88, respectively, mounted on rod member 84 for movement longitudinally thereof.

Bases 86 and 88 are each split at a zone 90 intermediate the lowermost extremity thereof, and each is provided with an elongated bore 92 for receiving rod member 84 therewithin. A screw 94 interconnects the portions formed on either side of zone 90 and clamps the corresponding base 86 or 88 to rod member 84. It is clear that each of the bases 86 and 88 is shiftably mounted along the length of rod member 84 toward and away from the corresponding side of the roll 12.

Base 88 threadably receives an elongated screw 96 which passes through an opening (not shown) in side wall 16 and projects outwardly therefrom. A guide 98 journals the outermost end of screw 96 and is movable along the proximal end of rod member 84. A handwheel 100 is rigid to screw 96 by means of a coupling shaft 102 and causes screw 96 to advance in opposed directions responsive to the rotation of handwheels 100 in vcorresponding opposite directions. Rotation of handwheel 100 causes base 88 to move toward and away from the corresponding side of roll 12 so that once the roller 80 is positioned against the corresponding side of roll 12, roller 82 may then be positioned against the corresponding side of roll 12 by advancing the same by rotation of handwheel 100. Rollers and 82 therefore provide guide structure for moving the web along a predetermined path as the same leaves roll 12 and, as shown in FIG. l, the web denoted by the numeral 104, leaves roll 12 tangentially of the latter and passes over a pair of horizontally spaced idler rollers 106 and 108 and thence upwardly to an idler roller 110 spaced above roller 108. Rollers 80 and 82 assist in maintaining the web 104 in predetermined positions on rollers 106 and 108 at all times so that theweb 104 is maintained in alignment with roller 110 for subsequent movement toward the printing press units adapted for receiving web 104.

Means is provided for biasing shaft 60 and thereby roller 12, in opposed directions, depending upon the location of shaft 60 relative to the ends of the corresponding racks 46. To this end, an elongated element 112 is pivotally mounted intermediate the ends thereof on a pin 114 extending outwardly from each of the walls 14 and 16, it being noted that there is an element 112 for each of walls 14 and 16.

Each element 112 is provided with an adapter 116 at one end thereof for bifurcating the end to receive the corresponding end of shaft 60. Each element 112 is reduced in thickness to provide a stretch 118 cooperating with the adapter 116 to form the bifurcated end of element 112, adapter 116 including a pair of parallel stretches 120 and 122, and intermediate stretch 124 coupling stretches 120 and 122.

A generally triangular segment 126 of rigid material is mounted on the opposite end of element 112 and is provided with a generally arcuate edge having teeth (not shown) thereon meshing with a link chain 128 as is clear in FGS. 1 and 2. One end of chain 128 is secured to segment 126 in spaced relationship to pin 114, and the opposite end of chain 128 is secured to the end of an elongated coil spring 130 secured at the opposite end thereof to a pin 132 mounted on and extending outwardly from the outer surface of the corresponding wall 14 or 16. Spring 130 is normally under tension so that chain 128 is urged in the direction of spring 130. When shaft 60 is disposed at the normally uppermost end of its path of travel, chain 128 is positioned on the lowermost side of pin 114. In this position, a force is applied to the opposite end of element 112 to bias shaft 60 upwardly in the direction opposed to the direction of downward movement thereof.

As shaft 60 moves downwardly over racks 46, the same reaches a point wherein chain 128 is disposed directly over pin 114. In this position, element 112 is substantially unbiased, since the force created by spring 130 passes directly through the axis of pivotal movement of each of the elements 112. As chain 128 moves onto the upper side of pivot pin 114, it is clear that the chain moves out of engagement with the teeth on segment 126 adjacent the axis of pivotal movement of element 112 so that in effect, the spring is exerting a restoring force on element 112 on the uppermost side of pin 114. In this manner, element 112 provides abias force for shaft 60 which is directed downwardly or in the direction of movement of shaft 60 over racks 46. It is evident that as the weight of roll 12 decreases responsive to the removal of the web 104 thereof, the weight becomes insulicient tol maintain roll 12 in frictional engagement with belt 74 to maintain the speed of rotation of roll 12. By virtue of the downward bias force on shaft 60 caused by element 112, roll 12 is suiciently biased against belt 74 to maintain the proper frictional force required to sustain the rotation of roll 12.

Each strip 54 carries a pair of stops 134 having projections 136 thereon extending outwardly from the corresponding strip 54 and engageable with the bifurcated end of the corresponding 'element 112 to thereby limit the path of travel of the latter.

Means for -driving sprocket 78 includes an elongated,

endless link chain 138 trained over sprocket 78 and over a pair of idler sprockets 140 and 142 rotatably mounted on wall 16 and one end of an elongated bar 144, respectively. Bar 144 is pivotally mounted by means rof a pin 146 on the outer surface of wall 16 yand sprocket 142 is biased into operating relationship with chain 138 by means of an elongated spring 148 secured to the opposite end of bar 144 and to the outer surface of wall 16 by pin 150. A sprocket 152 operably receives chain 138 and is rotatabl-e by virtue of being connected to an elongated shaft 154 extending through Wall 16 and operably coupled with a right angle gear mechanism 156 disposed on 'the inner surface of wall 16 by means of a platform 158. Gear mechanism 156 is operably coupled to the shaft (not shown) of a rotatable pulley 160 mounted for rotation about a horizontal axis, it being clear that the axis of revolution of pulley 160 is substantially normal to the axis of revolution of sprocket 152.

An endless, exible belt 162 is trained over pulley 160 and is operably coupled with a variable ratio pulley device device broadly denoted by the numeral 164. Device 164 includes a pair of relatively shiftable sheaves 166 and 168, the latter sheave being operably coupled with la spring (not shown) disposed within a hub 170 for biasing the sheaves 166 and 168 together.

A first plate 172 is secured to spaced angle irons 174 secured to the inner surfaces of walls 14 and 16 adjacent drive means 64 and above the latter. A second plate 176 is secured by means of ka pair of spaced angle irons 178, only one of which is shown, to the inner surfaces of walls 14 and 16, plates 172 and 176 being in horizontally spaced relationship and in substantial spanning relationship to walls 14 and 16.

The shaft of the pulley 160 is secured in suitable bearing means (not shown) mounted on the proximal face of plate 172. The shaft 186 of device 164, `spans the distance between plates 172 and 176 and is journalled in the latter by virtue of bearing means 182 and 184. Shaft 18() is in horizontally spaced relationship to the shaft of pulley 160 and also shaft 180 mounts thereon a pulley 186 adjacent hub 170 of device 164. Pulley 186 is operably coupled with a exible7 endless belt 188 which passes through an elongated slot 190 in the side of wall 14 and is operably coupled with a pulley 192 secured to the drive shaft 194 of a power source 196 in the nature of an electric motor. Source 196 is provided with a base 198 secured in any suitable manner on surface 18 so that pulley 192 is maintained in alignment with pulley 186.

A ring gear 200 is provided with a hub 202 which is rigid to the outermost end of shaft 180 for rotation therewith. Gear 286 is provided with circumferentially spaced teeth on the periphery thereof which are provided with convex, outermost surfaces, and the teeth on gear 200 are movable into meshing relationship with inwardly directed teeth -on the inner surface of an elongated sleeve 204 having an inner portion 206 press-fitted within the proximal end of an elongated tube 208. Tube 208 provides a coupling member between shaft 180 and the drive means Vof printing press units associated with structure so that the printing press units may be actuated responsive to the actuation of power source 196 to thereby preclude a separate power source for each of the printing press units.

Means for tensioning web 104, Iafter the same has been removed from roll 12, includes an elongated rod 21) which is rotatably mounted at the ends thereof in walls 14 and 16 and disposed adjacent the junctions of end edge 24 and top edge 28. A pair of arms 212 are secured to rod 218 adjacent the ends of the latter for rotation therewith, it being note-d that bearing means 214 at each end of rod 210, journal the ends of the latter on walls 14 and 16. As illustrated in FIG. l, the ends of arms 212 connected to rod 218, are split to provide zones 216 which permit the portions formed on either side of zones 216 to move together by the advancing of a bolt 218 secured to 6 said portions. Thus, arms 212 are rmly clamped to rod 210 to prevent relative motion therebetween.

An elongated, pneumatically actuated power device 220 is carried by wall 16 on the outer surface thereof and is operably coupled with rod 210 for 4rotating the latter in opposed directions. Device 220 includes a cylinder 222 having means for receiving a supply of air under pressure for kactuating a piston having a piston rod 224 extending outwardly from cylinder 222 and pivotally mounted at the outermost ends thereof to an ear 226 rigid to the proximal outer end of rod 210. Furthermore, cylinder 222 is pivotally mounted by means of a pin 228 on wall 16 for movement relative to the latter.

An extension 230 is secured to rod 210 between arms 212 thereon for rotati-on with rod 210, and a leg 232 is pivotally mounted at the outermost end of extension 230 in any suitable manner such as by a ball and socket joint. Leg 232 extends downwardly from extension 230 and is received within a sleeve 234 in any suitable manner such as by a ball and socket joint. Sleeve 234 is rigid to one end of Ia strap 236 which, together with a strap 238, mounts therebetween a pulley 240 for rotation about a pin 242 intermediate the ends of straps 236 and 238.

Straps 236 and 238 are rigid to an elongated shaft 244 which is journalled at the ends thereof in upright supports 246 and 248 secured to the uppermost margins of plates 172 land 176, respectively. Pulley 240 is normally in operable engagement with belt 162 and is provided for varying the tension on belt 162 responsive to the position of straps 236 and 238 relative to rod 210. As rod 210 rotates `about the longitudinal axis thereof, extension 230 is moved toward or away from belt 162. As extension 230 moves toward belt 162, the pulley 240 increases the tension on belt 162 to thereby separate sheaves 166 and 168 on device 164. Conversely, as extension 238 moves away from belt 162, pulley 240 relaxe-s the tension on belt 162 and sheaves 166 and 168 move together. In this manner, rotation of rod 210 is sufficient to control the speed of rotation of pulley 160 and thereby control the speed of rotation of roll 12.

A tensioning roller 250 is carried by arms 212 and subst-antially spans the distance therebetween, roller 250 being rotatably mounted on arms 212 by means of a shaft 252 carried at the ends of arms 212. An idler roller 254 is disposed in horizontally spaced relationship to idler roller and roller 250 is normally positioned between rollers 116 and 254 for tensioning the web 104 passing over roller 110, under roller 250 and over roller 254 as is illustrated in FIG. 1.

Side panels 256 and 258 are removably mounted on walls 14 and 16, respectively, by brackets 260 and 262 so that panels 256 and 258 are in outwardly spaced relationship to walls 14 and 16, as is clear in FIG. 3. Panels 256 and 258 span the distance between edges 24 and 26 and between edges 28 and 36 to provide an attractive exterior to structure 10 as well as concealing the various components mounted on the outer surfaces of walls 14 and 16. The uppermost margin of each of said panels 256 and 258 is provided with Ian inclined portion 264 which extends to the corresponding top edge 28.

Air valve means 266 and air gauge means 268 are carried by portion 264 corresponding to wall 16. An air line 270 places valve means 266 in fluid communication with cylinder 222 Iand a similar tube (not shown) operably interconnects gauge means 268 with air line 270 to indicate the pressure of the air in line 270. Valve means 266 is provided with a rotatable handle 272 externally of portion 264 and is constructed in a manner to increase the air pressure in line 270 when handle 272 is rotated in one direction and to decrease the air pressure in line 270 when handle 272 is rotated in the opposite direction. Valve means 266 is adapte-d to be operably coupled t-o a source of air under pressure. Valve means 266 is a bleeder type pressure regulator which maintains pressure at a given pressure. Rod 224 will be extended if the 7 path loop is slack. Tightening of the path loop will retract rod 224, the regulator bleeding olf the pressure generated by this motion. Thus, the tension in the path loop is sensibly constant regardless of its length.

By virtue of the control means including valve means 266 and gauge 268, the pressure of air in cylinder 222 may be accurately controlled to thereby control the tension applied to web 104 by roller 250.

In operation, the drum on which shaft 60 is rotatably disposed is initially press-lifted within the core 58 of roll 12 and the latter is then disposed between walls 14 and 16 by placing shaft 60 within slot 44 at the entrance of the slot in edges 26 of walls 14 and 16. Shaft 60 is supported at the ends thereofby strips 54 and is supported intermediate the ends thereof by pinions 62 which mesh with the teeth on racks 46. Rollers 80 and 82 are then caused to engage the corresponding sides of roll 12 adjacent the zone of removal of the web from the latter so as to properly align the web as the same moves tangentially oif roll 12 toward roller 106.

The web of roll 12 is then reeled out and is caused to pass below roller 106, below and around roller 108, upwardly to and over roller 110, downwardly toward and below roller 250, and then upwardly toward and over roller 254. After passing over roller 254, the web is directed to the processing units which are adapted to perform the various operations on the web, and which have Web drive means thereon.

Roll 12 is then permitted to gravitate along the inclined path defined by racks 46 until the periphery of roll 412 engages the belts 74 of drive means 64.

Air is supplied to the cylinder 222 to provide tension on web 104, and to this end, roller 250 is driven into engagement with web 104 by the actuation of the piston within cylinder 222. The pressure of the air within cylinder 222 may be accurately gauged so that a predetermined tension maybe placed on web 104 by roller 250.

Suitable control apparatus is provided for actuating power source 196 so that roll 12 may be rotated about the axis of shaft 60 by drive means 64 therefor.

Actuation of power source 196 causes the rotation of shaft 180, the rotation of device 164, pulley 160 and sprocket 78. Rotation of sprocket 78 causes shaft 66 to rotate to thereby drive belts 74 which are disposed in frictional engagement .with roll 12. The position of rod 210 determines the tension on belt 162 and thereby the speed of rotation of pulley 160, thus controlling the speed of rotation of roll 12, depending upon the requirements of the units which are fed by web 104. It is noted that the drive means of each of the units associated with web 104 is actuated by the rotation of tube 208 which is in turn operably coupled to shaft 180.

A change in tension in the web is sensed by the tensioning means comprising arm 212 and roller 250 so that the leg 232 is moved upwardly or downwardly to thereby relax or increase the tension on belt 162 and thus cause the sheaves 166 and 168 of device 164 to move toward or away from each other respectively. If the tension of the web is increased, arm 212 moves upwardly and the tension on lbelt 162 is relaxed to move sheaves 166 and 168 together. This action is sufficient to increase the speed of rotation of pulley 160 and thereby the speed of rotation of roll 12 to thereby compensate for the increased demand for web 104 caused by the increased tension. Conversely, if the tension of the web is decreased, the rod 210 is rotated so that leg 232 moves downwardly and thus increases the tension =on belt 162. When this occurs, the sheaves 166 and 168 move apart and the speed of rotation of pulley 160 decreases.

It is noted that the power source 196 is operably coupled with both the roll 12 and the units fed from the web on roll 12 so that actuation of power source 196 places the roll drive means 64 and the individual drive means of the various units in operation simultaneously. Therefore, there can be no accumulation of web by rotating roll 12 when the units are not in operation. Further, it is to be noted that the roll drive means 64 is initially set to deliver web 104 to the units at substantially the same speed at which the web 104 is fed into the units.

Roll 12 will continue to gravitate toward belt 74 as the diameter of roll 12 decreases, due to the removal of web therefrom. When the diameter of the roll decreases to a certain value, element 112 adds a biasing force to shaft 60 to augment the weight of roll 12 and thereby maintain the latter in suicient frictional engagement with belts 74 to properly remove web 104 therefrom.

Attention is called to the fact that the use of toothed belts 74 assures a rate of belt movement directly proportional to input at sprocket 78. The rolls, when half or more unreeled, are heavy enough to maintain full driven Contact without slippage, with the belts. The bias force derived from elements 112, assures continued reliable contact as the roll gets lighter. Therefore, the construction shown assures that output from the roll is directly proportional to the input revolutions at sprocket 7 8.

Further attention is called to the feedback loop based on input and output at the path loop between rollers and 254. The force exerted `by tensioning roller 250 is substantially constant regardless of its position. `It assumes any position solely as a function of the difference, if any, between web speed at the take-off point from the roller, and the web speed at the supply point for the unit (which may be immediately to the left of roller 254). Movement of the tensioning roller in either direction adjusts the diameter of the device 164 to nullify the change in path loop length. In use, the speed change effected by the device is rarely greater than plus or minus 1%, but this is ample compensation to keep the device in very close, steady-stream operation.

This invention is not to be limited by the embodiment shown in the drawings and described in the description, which is given by way of example, and not of limitation, but only in accordance with the appended claims.

We claim:

1. In web processing apparatus adapted to be fed from an elongated web initially disposed in the form of a roll, means for handling said roll to remove the web therefrom to thereby permit the web to move into operating relationship with a portion of said apparatus, said means cornprising support structure including a pair of spaced walls; a shaft adapted to be rotatably secured to said roll at the center thereof and to extend outwardly from opposed sides of said roll; inclined track means carried by each of the walls and normally engaging a corresponding end of the shaft in supporting relationship thereto for mounting said shaft and thereby said roll between said walls for movement along an inclined path under the action of gravity; roll drive means carried by said support structure adjacent the normally lowermost end of said track means and engageable with said roll at the periphery thereof for rotating said roll in a direction to permit the removal of said web therefrom, said shaft and thereby said roll being movable along said path responsive to the decrease in diameter of the roll to maintain said roll drive means in driving relationship with said roll as the web is removed therefrom; and guide means carried by said walls adjacent the Zone of removal of said web from the roll and engageable with the latter for directing the web along a path aligned with said portion of the apparatus and for maintaining the roll in a predetermined position as the web is removed therefrom.

2. In web processing apparatus as set forth in claim 1, wherein said guide means includes an elongated rod secured to and spanning the distance between said walls, and roller means carried by said rod on opposed sides of the roll and normally engaging the latter for preventing lateral movement of the web as the latter moves longitudinally.

3. In web processing apparatus as set forth in claim 2, wherein said roller means includes a base releasably secured to said rod and movable longitudinally thereof, and a roller carried by said base for rotation about an axis substantially normal to the longitudinal axis of the rod, said rollers normally engaging corresponding sides of said roll at said zone.

4. In web processing apparatus as set forth in claim 3, wherein is included screw means carried by at least one of said walls for threadably mounting the corresponding base on said one wall, and means operably coupled with said screw means for advancing the latter in opposed directions to thereby adjust the position of the ,corresponding base -on said rod.

5. In web iprocessing apparatus adapted to be `fed from an elongated web initially disposed in the form of a roll, means for handling said roll to remove the web therefrom to thereby permit the web to move into operating relationship with a portion of said apparatus, said means comprising support structure including a pair of spaced walls; a shaft adapted to be rotatably secured to said roll at the center thereof and to extend outwardly from opposed sides of said roll; inclined track means carried by each of the walls and normally engaging a corresponding end of the shaft in supporting relationship thereto for mounting said slaft and thereby said roll between said walls for movement along an inclined path under the action of gravity; roll drive means carried by said support structure adjacent the normally lowermost end of said track means and engageable with said roll at the periphery thereof for rotating said roll in a direction to permit the removal of said web therefrom, said shaft and thereby said roll being movable along said path responsive to the decrease in diameter of the roll to maintain said roll drive means in driving relationship with said roll as the web is removed therefrom; and means carried by said walls and engageable with the shaft for biasing said shaft in one direction when said shaft is disposed on one side of a predetermined position on said inclined path and for biasing the shaft in the opposite direction when said shaft is disposed on the opposite side of said position.

6. In web processing apparatus adapted to be fed from an elongated web initially disposed in the form of a roll, means for handling said roll to remove the web therefrom to thereby permit the web to move into operating relationship with a portion of said apparatus, said means `comprising support structure including a pair of spaced walls; a shaft adapted to be rotatably secured to said roll at the center thereof and to extend outwardly from opposed sides of said roll, inclined track means carried by each of the Walls and normally engaging'a corresponding end of the shaft in supporting relationship theneto for mounting said shaft and thereby said roll between said walls for movement along an inclined path under the action of gravity; roll drive means carried by said support structure adjacent the normally lowermost end of said track means and engageable with said roll at the periphery thereof for rotating said roll in a direction to permit the removal of said web therefrom, said shaft and thereby said roll being movable along said path responsive to the decrease in diameter of lthe .roll .to maintain said roll drive means in driving relationship with said roll as the web is removed therefrom; land an elongated element pivotally mounted intermediate the ends thereof on a corresponding wall, said element being provided with yieldable means adjacent one end thereof and movable on opposed sides of the point of pivotal mounting thereof with the corresponding wall responsive to the movement of said shaft along said inclined path for urging said element in one direction when said yieldable means is on one side of said point and for urging said element in the opposite direction when said yieldable means is on the opposite side of said point.

7. In web processing apparatus as set forth in claim 6, wherein each of said elements is bifurcated at the opposite end thereof for receiving the corresponding end of said shaft, and including spaced stop means carried by each 10 wall across the path of travel of said element for limiting the movement of said element in said opposed directions.

8. In web processing apparatus as set forth in claim 6, wherein said yieldable means includes an elongated coil spring secured at one end thereof to the corresponding wall and mounted at the opposite end thereof on said one end of said element for movement on opposed sides of said point.

9. In web iprocessing apparatus as set forth in claim 8, wherein is included a projection on said element at said one end thereof and having a peripheral edge provided with a number of spaced teeth thereon, and a flexible chain carried by said projection and operably coupled with said teeth thereon, one end of said chain being secured to the opposite end of said spring for moving the latter on opposite sides of said point responsive to the swinging movement of said projection about said point as said shaft moves along said inclined path.

10. In web processing apparatus adapted to be fed from an elongated web initially disposed in the form of a roll and provided with at least one unit adapted for receiving said web and performing a distinct operation thereon as the web passes therethrough at one of a number of preselected speeds, means for handling said roll to remove the web therefrom and to dispose said web for movement into operating relationship with said unit, said means including support structure; shaft means shiftably carried by said support structure and adapted to be rotatably mounted on the roll at the center thereof for rotatably and shiftably mounting said roll on said support structure; roll drive means carried by said support structure and engageable with said roll at the periphery thereof for rotating the roll in a direction to permit the removal of said web therefrom, said shaft means being biased for movement toward said roll drive means to maintain the latter in driving relationship to said roll as said web is removed therefrom; and web-tensioning means carried by said support structure for applying a predetermined tension to the web removed from the ro-ll, said Webtensioning means including an elongated rod rotatably mounted Ion said structure, an arm rigid to said rod for rotation therewith, and having roller means thereon engageable with said web for applying said predetermined tension, and power-actuated means carried by the structure and operably coupled with said rod for applying a rotational force to the latter, said po-wer-actuated means being disposed for permitting the rod to rotate relative thereto responsive to the variation of tension on the web when the speed of the latter is varied and as the web passes through said unit, said roll drive means having variable speed-actuating means thereon for varying the speed of rotation of said roll, said web-tensioning means being disposed for sensing the web speed changes of said unit and being operably coupled with said variable speedactuating means for varying the rotational speed of said roll responsive to the change in speed of the web passing through said unit.

11. In web processing apparatus as set forth in claim 10, wherein is included an extension rigid to said rod and operably coupled with said variable speed-actuating means for operating the latter to vary the speed of said roll responsive to the rotation of said rod caused by the variation in tension on said web when the speed of the latter is varied as the web passes through said unit.

12. In web processing apparatus as set forth in claim 11, wherein said variable speed-actuating means includes a variable ratio pulley rotatably mounted on said structure and an end-less belt operably coupled with said variable ratio pulley, said extension being movable toward and away from said belt and engaging the latter to vary the tension thereon to thereby vary the effective diameter of the pulley responsive to the rotation of said rod.

(References on following page) 1 1 References Cited by the Examiner 2,558,761 7/1951 Kentis 242-571 UNITED STATES PATENTS 2,881,984 4/ 1959 Dyken 242-55 .1 Savery A Huck 12/ 1916 Walser et al. 242-76 2/1934 Broadmeyer 242 58 6 5 MERVIN STEIN, Primary Examzner. 9/ 1950 Scheuermann et a1. RUSSELL C. MADER, Examiner. 

1. IN WEB PROCESSING APPARATUS ADAPTED TO BE FED FROM AN ELONGATED WEB INITIALLY DISPOSED IN THE FORM OF A ROLL, MEANS FOR HANDLING SAID ROLL TO REMOVE THE WEB THEREFROM TO THEREBY PERMIT THE WEB TO MOVE INTO OPERATING RELATIONSHIP WITH A PORTION OF SAID APPARATUS, SAID MEANS COMPRISING SUPPORT STRUCTURE INCLUDING A PAIR OF SPACED WALLS; A SHAFT ADAPTED TO BE ROTATABLY SECURED TO SAID ROLL AT THE CENTER THEREOF AND TO EXTEND OUTWARDLY FROM OPPOSED SIDES OF SAID ROLL; INCLINED TRACK MEANS CARRIED BY EACH OF THE WALLS AND NORMALLY ENGAGING A CORRESPONDING END OF THE SHAFT IN SUPPORTING RELATIONSHIP THERETO FOR MOUNTING SAID SHAFT AND THEREBY SAID ROLL BETWEEN SAID WALLS FOR MOVEMENT ALONG AN INCLINED PATH UNDER THE ACTION OF GRAVITY; ROLL DRIVE MEANS CARRIED BY SAID SUPPORT STRUCTURE ADJACENT THE NORMALLY LOWERMOST END OF SAID TRACK MEANS AND ENGAGEABLE WITH SAID ROLL AT THE PERIPHERY THEREOF FOR ROTATING SAID ROLL IN A DIRECTION TO PERMIT THE REMOVAL OF SAID WEB THEREFROM, SAID SHAFT AND THEREBY SAID ROLL BEING MOVABLE ALONG SAID PATH RESPONSIVE TO THE DECREASE IN DIAMETER OF THE ROLL TO MAINTAIN SAID ROLL DRIVE MEANS IN DRIVING RELATIONSHIP WITH SAID ROLL AS THE WEB IS REMOVED THEREFROM; AND GUIDE MEANS CARRIED BY SAID WALLS ADJACENT THE ZONE OF REMOVAL OF SAID WEB FROM THE ROLL AND ENGAGEABLE WITH THE LATTER FOR DIRECTING THE WEB ALONG A PATH ALIGNED WITH SAID PORTION OF THE APPARATUS AND FOR MAINTAINING THE ROLL IN A PREDETERMINED POSITION AS THE WEB IS REMOVED THEREFROM. 